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THERMAL DEVICES, DEVICES FOR HEATING AIR AND OTHER GAS-FUEL MEDIA AND THEIR APPLICATION
INVENTION
Patent of the Russian Federation RU2287708

ENERGY INSTALLATION FOR AUTONOMOUS ENERGY SUPPLY

The name of the inventor: Written Vladimir Leonidovich (RU)
The name of the patent owner: Written Vladimir Leonidovich (RU)
Address for correspondence: 141103, Moscow Region, Shchelkovo-3, ul.Supruna, 1, ap. 40, V.L. Written
Date of commencement of the patent: 2005.03.21

The invention relates to heat power engineering. In a gas turbine power plant with air extraction behind the compressor followed by its heating by exhaust gases and expansion in a free air turbine, an additional working fluid is water that is converted into superheated steam by the energy of the off-gases, including air leaving the air turbine, whose temperature is not less than 170 ° C . The power plant has low values ​​of the parameters of the working process: the compression ratio in the compressor is less than 12; Gas temperature in front of the turbine is less than 1400 K; Water consumption is less than 9% of the air flow with an effective efficiency of 45-50%. The invention allows generation of thermal energy in the form of heated water (~30%) and air (~10%) in addition to electric energy (~50%). Hot air is clean and can be used for air conditioning and heating of living quarters.

DESCRIPTION OF THE INVENTION

The invention relates to heat power engineering.

The aim of the invention is to solve the problem of autonomous power supply of industrial enterprises and residential complexes.

To ensure the thermal and electrical energy of places remote from thermal power plants and power lines, diesel power stations ( or the gas turbine drives made on the basis of a diesel-electric power station) are used, as a rule, to use diesel generators (Big Soviet Encyclopedia, Third Edition, Vol. 8. M: Soviet Encyclopedia, 1972, p.253) Aviation Technologies (VVKuprik, Conversion of Aircraft Engines to a Gas Turbine Drive for Land Installations, Conversion in Mechanical Engineering, No. 5, 2003, p.17-22) . Stationary diesel power plants have a fairly high efficiency (the efficiency of modern diesel engines reaches 45%), but their capacity (not more than 3 MW) and the motor resource are insufficient to solve the problem of power supply to industrial enterprises. Gas-turbine drives (GTU) in contrast have high power (10-25 MW) and a large motor resource (more than 50,000 h), but their efficiency is lower than that of diesel engines (an effective efficiency of less than 38%). In addition, the cost of manufacturing gas turbine drives because of the high values ​​of the parameters of the working process is high.

At present, much attention is paid to the development of combined-cycle plants (Olkhovsky GG Gas Turbine Combined-Gas Installations in Russia., Heat Power Engineering, 1999, No. 1, p.2-5) . Steam-gas plants have high efficiency (50-55%), which are achieved due to extremely high temperatures (1500-1700 K) and pressures (more than 30 atm) in front of the turbine, which makes gas-vapor installations very expensive in production and operation, and significantly limits Service life.

There are known gas turbine engines with heat recovery (Theory and calculation of air-jet engines, edited by SM Shlyakhtenko, M: Mechanical Engineering, 1987, p.353, pic.11.3) . In these engines, a gas-air heat exchanger (air heater) is installed behind the engine turbine.

Gas-turbine plants are known with the selection of air behind the compressor and its subsequent use for driving an air turbine (UK Patent No. 1201526, IPC F 02 K 3/02 GAS TURBINE POWER UNITS G. Garraway, 1970) .

The essence of the invention is that the energy of the fuel released during its combustion is distributed to a large mass of the working fluid (air and water) of the GTU, which allows it to lower the temperature of the working fluid (increase the service life) And, as a consequence, make the manufacture and operation of the GTU cheaper. The technical effect is achieved by transferring the main part of the energy generated by the turbocharger to the air entering the air turbine. Transmission of energy is carried out by compressing air in the compressor and then heating it with gases escaping from the turbocompressor. To increase the mass of the working fluid (air and water) in the output channels of the turbocharger and air turbine, a superheater and a heat exchanger-evaporator are installed that partially convert the energy of the waste gases to the energy of water vapor that enters the mixing chamber of the turbocharger and is converted to additional mechanical work on the turbocharger shaft . The latter is possible if the air temperature behind the air turbine is not less than 170 ° С.

ENERGY INSTALLATION FOR AUTONOMOUS ENERGY SUPPLY

1 is a schematic diagram of a power plant

ENERGY INSTALLATION FOR AUTONOMOUS ENERGY SUPPLY

2 is a schematic diagram of a power plant

3 depicts the dependence of the effective efficiency and specific power on the gas temperature in front of the turbocharger turbine

4 shows the interdependence of the operating parameters of the power plant

5 shows a diagram of the energy distribution in a gas turbine

The power plant (FIG. 1) consists of a turbocharger comprising a compressor 1. The turbocharger comprises a combustion chamber 2 and a mixing chamber 3 which are arranged in series between the compressor and a combined-cycle turbine 4. The installation comprises an air heater 5 located in the outlet of the turbocharger connected On the one hand with the cavity behind the compressor, and on the other side with the input receiver of the air turbine 7. The installation contains a superheater 6 located in the outlet of the turbocharger behind the hot-air heater. The installation contains a heat exchanger-evaporator, located in the outlet channel of the air turbine. The superheater and the heat exchanger-evaporator are connected to the mixing chamber of the turbocharger via a steam mixer 9.

The installation also includes pumps (n) standing in the lines for injecting water and fuel, respectively, of a generator that converts mechanical work on the shaft of an air turbine into electrical energy. The air heater 5 is structurally designed as a gas-air heat exchanger. The superheater 6 and the heat exchanger-evaporator 8 are structurally designed as liquid-gas heat exchangers.

In the output channel of the turbocharger, an economizer can be installed, which heats the water used to power the superheater, the heat exchanger-evaporator and external consumers.

Between the stove and the superheater, a fuel evaporator can be mounted, connected on one side to the fuel source, and on the other side to the combustion chamber of the turbocharger.

The inlet to the compressor can be supplied with water.

The pressure of steam entering the mixing chamber of the turbocharger is higher than the pressure of the gas entering the same mixing chamber by 10-30%.

Operation of the installation is as follows. Air through the input device enters the compressor 1 for compression. The air compressed to a given pressure (compression ratio not more than 15) is divided into two streams: the first flow is directed to the combustion chamber 3 and the second one to the water heater 5.

In the combustion chamber, air is mixed with fuel, which is pumped into the combustion chamber by a pump. The composition of the air-fuel mixture in the combustion chamber approaches a stoichiometric one, which, when the mixture burns, leads to an increase in the gas temperature above the turbine blades that are permissible in strength. From the combustion chamber 2, the hot gas is directed to the mixing chamber 3 where simultaneously superheated steam is directed from the superheater 6 and the heat exchanger-evaporator 8 mixed in the mixer 9. In the mixing chamber 3, the hot gas and superheated steam are mixed, The values ​​admissible for the strength conditions of the turbine blades, and the enthalpy of the working fluid is increased. From the mixing chamber 3, the working fluid (a mixture of steam and gas) flows into the turbine 4 of the compressor drive, and then into the air heater 5 and the superheater 6. In the superheater 6, the working medium gives some of its energy to the water moving through the heat exchanger channels, turning it into superheated steam. Superheated steam enters the mixer 9, and the working fluid is removed to the atmosphere.

In the air heater 5, the air, as a result of heat exchange with the gases leaving the turbocharger, is heated, and then it enters the turbine 7, which performs mechanical work that is converted into electric energy in the generator. The air temperature at the outlet of the turbine 7 is maintained at least equal to the boiling point of the water in the heat exchanger-evaporator 8 (the minimum temperature at which the elements of the unit can be operated together is 170 ° C). After passing through the turbine 7, air releases some of its energy to the water moving in the heat exchanger-evaporator 8, turning it into dry steam. The dry steam enters the mixer 9, and the air is removed to the atmosphere (it flows to the external consumer).

There are ways to increase the efficiency of the installation (FIG. 2):

Methods based on a more complete use of energy from waste gases, for example, using an economizer 10 installed in the outlet of the turbocharger, and a recovery boiler (CG) or using a fuel evaporator 11 installed between the hot-runner 5 and the superheater 6. The economizer operates in Increase the efficiency of heat exchange by using more than in the superheater water consumption (additional water flow is provided by external consumers). The principle of the fuel evaporator is that the energy of waste gases is used for evaporation and fuel heating, which is much more advantageous than the use of gas energy in the combustion chamber. Given that the relative fuel consumption in the combustion chamber of the power plant is 4-6%, an increase in efficiency from the use of a fuel evaporator is 3-4%.

A method based on increasing the efficiency of the axial compressor (reducing the work of compression) by cooling the compressed air. There is a known method of forcing a gas turbine plant by injecting water into the compressor inlet (Theory and calculation of air-jet engines., Ed., S.Shlyakhtenko, M: Mechanical Engineering, 1987, p. 374). Experiments show that under the conditions of the axial compressor GTE evaporates from 30 to 50% of the water injected in front of the compressor. The rest of the water evaporates in the combustion chamber. Air cooling in the axial compressor due to the evaporation of water leads to an increase in the efficiency of the compressor, which manifests itself in an increase in the air flow. Evaporation of the remaining water in the combustion chamber leads to the absorption of part of the energy of hot gases, which leads to a decrease in the economy of the engine. In the power plant, most of the air (60-70%) enters the air turbine and, correspondingly, the proportion of water entering the combustion chamber is 3-4 times less than in conventional gas turbines. If to consider as a whole, the positive effect of increasing the air flow through the compressor (air turbine) is higher than the negative effect of evaporation of a small amount of water in the combustion chamber and the efficiency of the installation increases. Quantitative relationships between the efficiency and the mass of injected water are established experimentally, based on the condition of ensuring a stable operation of the compressor.

The method based on compensation of gas pressure losses along the turbocharger path due to the use of excess vapor pressure. Gas ejectors are known which allow increasing the pressure of the ejected gas (VK Shchukin, II Kalmykov, Gas-Jet Compressors, M: Mechanical Engineering, 1963, 145 pp.). The use of a gas ejector when mixing steam and gas in the mixing chamber 3 allows the pressure of the mixture above the turbine to be higher than the pressure of the air behind the compressor at a vapor pressure higher than the gas pressure by 10-30%.

To assess the effectiveness of the proposed technical solution, a gas-dynamic calculation of the power plant was performed (FIG. 2, without feeding water to the compressor inlet). The calculation is performed for standard conditions (tn = 15 ° C and pH = 760 mm Hg). In this case, the losses are taken into account by the corresponding efficiency and pressure loss factors, namely: compressor efficiency - 0.86; Efficiency of turbines - 0,94; Loss of pressure: 0.5% in the input device, 3% in the combustion chamber, absent in the mixing chamber, 3% in the air heater, 3% in the superheater and heat exchanger and 1% in the economizer. The gas temperature at the outlet of the superheater and the heat exchanger-evaporator is 100 ° C. The fuel is kerosene.

FIG. 3 shows the dependence of the plant's power characteristics: effective efficiency E and the specific power Ne (the power per kilogram of air flow) from the gas temperature in front of the turbocharger turbine. The values ​​of the excess air factor in the combustion chamber Kc . It can be seen that the unit has high efficiency (more than 42%) with relatively low gas temperatures in front of the turbine (1200-1400K).

FIG. 4 shows the combinations of the parameters of the working process of the power plant: the degree of air compression in the compressor PK, the relative (in relation to the air flow rate) of the flow rate t, the gas temperature in front of the turbine Tr. It can be seen that for all T2, which characterize the technological level of the GTU fabrication, PK and m remain low.

Calculation studies and show that the effect of pressure losses along the installation path due to the features of its gas-dynamic circuit practically does not affect the effective efficiency of the installation.

The combination of these qualities makes the power plant of this type very attractive for industrial production and operation, since, as shown in Fig. 3 and Fig. 4, the installation scheme does not impose strict requirements on operating parameters and guarantees high efficiency and a motor resource.

In accordance with the principle of operation, the installation (FIG. 2) generates, in addition to electrical energy, thermal energy: hot water and hot air, and losses (gas and condensate emitted to the atmosphere, air heated by contact with the structure). FIG. 5 shows a distribution diagram of various types of energy generated by the installation as a function of the gas temperature in front of the turbocharger turbine. It can be seen that the overall efficiency of the installation (taking into account the useful thermal energy) is about 90%. In this case, in contrast to known plants, a considerable proportion (~ 10%) of hot air enters the composition of useful thermal energy. The availability of a sufficient amount of clean heated air, and its share can be increased due to the share of electric energy, allows the use of secondary air in the air conditioning and heating systems of residential premises, which is much more environmentally friendly, cheaper and more practical than steam heating. If necessary, the energy of hot air due to the lowering of the temperature at the outlet from the heat exchanger-evaporator 8 can be transformed into electric energy. However, the overall efficiency is reduced by 8-10%, while the effective efficiency increases by only 2-3%.

Using the technological and constructive reserve, namely: increasing the efficiency of the compressor and turbines, increasing the gas temperature before the turbine, increasing the efficiency of the heat exchangers, using water injection at the compressor inlet, using the ejector in the mixing chamber of the turbocharger allows, as estimates show, The effective efficiency of the installation is more than 60%, which is advisable if there is an economic justification (there is an increase in the cost of fuel).

CLAIM

1. An energy plant consisting of a turbocharger with combustion and mixing chambers that are arranged in series between the compressor and the turbine, an air turbine, an air heater located in the outlet of the turbocharger connected on one side to the cavity behind the compressor and, on the other hand, to the inlet air receiver Turbine, superheater located in the outlet of the turbocharger behind the heater, the heat exchanger-evaporator located in the outlet channel of the air turbine, characterized in that the superheater and the heat exchanger-evaporator are connected to the mixing chamber of the turbocharger and the air outlet temperature of the air turbine is not less than 170 ° FROM.

2. The power plant according to claim 1, characterized in that an economizer is installed behind the superheater in the outlet channel of the turbocharger, which heats the water used to power the superheater, the evaporator heat exchanger and external consumers.

3. The power plant according to claim 1, characterized in that a fuel evaporator is connected between the heater and the superheater, connected on one side to the fuel source, and on the other side to the combustion chamber of the turbocharger.

4. The power plant according to claim 1, characterized in that water is supplied to the compressor inlet.

5. The power plant according to claim 1, characterized in that the pressure of the steam entering the mixing chamber of the turbocharger is higher than the pressure of the gas entering the same mixing chamber by 10-30%.

print version
Date of publication 07.12.2006гг